Control architecture for output torque shaping and motor torque determination for a hybrid powertrain system

ABSTRACT

A powertrain system includes a transmission device operative to transfer power between an input member and a plurality of torque machines and an output member. The torque machines are connected to an energy storage device and the transmission device is operative in one of a plurality of operating range states. A method for controlling the powertrain system includes monitoring available power from the energy storage device, determining system constraints, determining constraints on an output torque to the output member based upon the system constraints and the available power from the energy storage device, determining an operator torque request, determining an output torque command based upon the constraints on the output torque and the operator torque request, and determining preferred torque commands for each of the torque machines based upon the output torque command.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No. 60/985,243 filed on Nov. 4, 2007 which is hereby incorporated herein by reference.

TECHNICAL FIELD

This disclosure pertains to control systems for hybrid powertrain systems.

BACKGROUND

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

Known hybrid powertrain architectures can include multiple torque-generative devices, including internal combustion engines and non-combustion machines, e.g., electric machines, which can transmit torque to an output member preferably through a transmission device. One exemplary hybrid powertrain includes a two-mode, compound-split, electro-mechanical transmission which utilizes an input member for receiving tractive torque from a prime mover power source, preferably an internal combustion engine, and an output member. The output member can be operatively connected to a driveline for a motor vehicle for transmitting tractive torque thereto. Torque machines, e.g., electric machines operative as motors or generators, can generate torque inputs to the transmission independently of a torque input from the internal combustion engine. The torque machines may transform vehicle kinetic energy transmitted through the vehicle driveline to energy that is storable in an energy storage device. A control system monitors various inputs from the vehicle and the operator and provides operational control of the hybrid powertrain, including controlling transmission operating state and gear shifting, controlling the torque-generative devices, and regulating the power interchange among the energy storage device and the machines to manage outputs of the transmission, including torque and rotational speed.

SUMMARY

A powertrain system includes a transmission device operative to transfer power between an input member and a plurality of torque machines and an output member. The torque machines are connected to an energy storage device and the transmission device is operative in one of a plurality of operating range states. A method for controlling the powertrain system includes monitoring available power from the energy storage device, determining system constraints, determining constraints on an output torque to the output member based upon the system constraints and the available power from the energy storage device, determining an operator torque request, determining an output torque command based upon the constraints on the output torque and the operator torque request, and determining preferred torque commands for each of the torque machines based upon the output torque command.

BRIEF DESCRIPTION OF THE DRAWINGS

One or more embodiments will now be described, by way of example, with reference to the accompanying drawings, in which:

FIG. 1 is a schematic diagram of an exemplary hybrid powertrain, in accordance with the present disclosure;

FIG. 2 is a schematic diagram of an exemplary architecture for a control system and hybrid powertrain, in accordance with the present disclosure; and

FIGS. 3-7 are schematic flow diagrams of a control system architecture for controlling and managing torque in a hybrid powertrain system, in accordance with the present disclosure.

DETAILED DESCRIPTION

Referring now to the drawings, wherein the showings are for the purpose of illustrating certain exemplary embodiments only and not for the purpose of limiting the same, FIGS. 1 and 2 depict an exemplary hybrid powertrain. The exemplary hybrid powertrain in accordance with the present disclosure is depicted in FIG. 1, comprising a two-mode, compound-split, electro-mechanical hybrid transmission 10 operatively connected to an engine 14 and torque machines comprising first and second electric machines (‘MG-A’) 56 and (‘MG-B’) 72. The engine 14 and first and second electric machines 56 and 72 each generate mechanical power which can be transferred to the transmission 10. The power generated by the engine 14 and the first and second electric machines 56 and 72 and transferred to the transmission 10 is described in terms of input and motor torques, referred to herein as T_(I), T_(A), and T_(B) respectively, and speed, referred to herein as N_(I), N_(A), and N_(B), respectively.

The exemplary engine 14 comprises a multi-cylinder internal combustion engine selectively operative in several states to transfer torque to the transmission 10 via an input shaft 12, and can be either a spark-ignition or a compression-ignition engine. The engine 14 includes a crankshaft (not shown) operatively coupled to the input shaft 12 of the transmission 10. A rotational speed sensor 11 monitors rotational speed of the input shaft 12. Power output from the engine 14, comprising rotational speed and engine torque, can differ from the input speed N_(I) and the input torque T_(I) to the transmission 10 due to placement of torque-consuming components on the input shaft 12 between the engine 14 and the transmission 10, e.g., a hydraulic pump (not shown) and/or a torque management device (not shown).

The exemplary transmission 10 comprises three planetary-gear sets 24, 26 and 28, and four selectively engageable torque-transferring devices, i.e., clutches C1 70, C2 62, C3 73, and C4 75. As used herein, clutches refer to any type of friction torque transfer device including single or compound plate clutches or packs, band clutches, and brakes, for example. A hydraulic control circuit (‘HYD’) 42, preferably controlled by a transmission control module (hereafter ‘TCM’) 17, is operative to control clutch states. Clutches C2 62 and C4 75 preferably comprise hydraulically-applied rotating friction clutches. Clutches C1 70 and C3 73 preferably comprise hydraulically-controlled stationary devices that can be selectively grounded to a transmission case 68. Each of the clutches C1 70, C2 62, C3 73, and C4 75 is preferably hydraulically applied, selectively receiving pressurized hydraulic fluid via the hydraulic control circuit 42.

The first and second electric machines 56 and 72 preferably comprise three-phase AC machines, each including a stator (not shown) and a rotor (not shown), and respective resolvers 80 and 82. The motor stator for each machine is grounded to an outer portion of the transmission case 68, and includes a stator core with coiled electrical windings extending therefrom. The rotor for the first electric machine 56 is supported on a hub plate gear that is operatively attached to shaft 60 via the second planetary gear set 26. The rotor for the second electric machine 72 is fixedly attached to a sleeve shaft hub 66.

Each of the resolvers 80 and 82 preferably comprises a variable reluctance device including a resolver stator (not shown) and a resolver rotor (not shown). The resolvers 80 and 82 are appropriately positioned and assembled on respective ones of the first and second electric machines 56 and 72. Stators of respective ones of the resolvers 80 and 82 are operatively connected to one of the stators for the first and second electric machines 56 and 72. The resolver rotors are operatively connected to the rotor for the corresponding first and second electric machines 56 and 72. Each of the resolvers 80 and 82 is signally and operatively connected to a transmission power inverter control module (hereafter ‘TPIM’) 19, and each senses and monitors rotational position of the resolver rotor relative to the resolver stator, thus monitoring rotational position of respective ones of first and second electric machines 56 and 72. Additionally, the signals output from the resolvers 80 and 82 are interpreted to provide the rotational speeds for first and second electric machines 56 and 72, i.e., N_(A) and N_(B), respectively.

The transmission 10 includes an output member 64, e.g. a shaft, which is operably connected to a driveline 90 for a vehicle (not shown), to provide output power to the driveline 90 that is transferred to vehicle wheels 93, one of which is shown in FIG. 1. The output power at the output member 64 is characterized in terms of an output rotational speed N_(O) and an output torque T_(O). A transmission output speed sensor 84 monitors rotational speed and rotational direction of the output member 64. Each of the vehicle wheels 93 is preferably equipped with a sensor 94 adapted to monitor wheel speed, the output of which is monitored by a control module of a distributed control module system described with respect to FIG. 2, to determine vehicle speed, and absolute and relative wheel speeds for braking control, traction control, and vehicle acceleration management.

The input torque from the engine 14 and the motor torques from the first and second electric machines 56 and 72 (T_(I), T_(A), and T_(B) respectively) are generated as a result of energy conversion from fuel or electrical potential stored in an electrical energy storage device (hereafter ‘ESD’) 74. The ESD 74 is high voltage DC-coupled to the TPIM 19 via DC transfer conductors 27. The transfer conductors 27 include a contactor switch 38. When the contactor switch 38 is closed, under normal operation, electric current can flow between the ESD 74 and the TPIM 19. When the contactor switch 38 is opened electric current flow between the ESD 74 and the TPIM 19 is interrupted. The TPIM 19 transmits electrical power to and from the first electric machine 56 by transfer conductors 29, and the TPIM 19 similarly transmits electrical power to and from the second electric machine 72 by transfer conductors 31 to meet the torque commands for the first and second electric machines 56 and 72 in response to the motor torque commands T_(A) and T_(B). Electrical current is transmitted to and from the ESD 74 in accordance with whether the ESD 74 is being charged or discharged.

The TPIM 19 includes the pair of power inverters (not shown) and respective motor control modules (not shown) configured to receive the motor torque commands and control inverter states therefrom for providing motor drive or regeneration functionality to meet the commanded motor torques T_(A) and T_(B). The power inverters comprise known complementary three-phase power electronics devices, and each includes a plurality of insulated gate bipolar transistors (not shown) for converting DC power from the ESD 74 to AC power for powering respective ones of the first and second electric machines 56 and 72, by switching at high frequencies. The insulated gate bipolar transistors form a switch mode power supply configured to receive control commands. There is typically one pair of insulated gate bipolar transistors for each phase of each of the three-phase electric machines. States of the insulated gate bipolar transistors are controlled to provide motor drive mechanical power generation or electric power regeneration functionality. The three-phase inverters receive or supply DC electric power via DC transfer conductors 27 and transform it to or from three-phase AC power, which is conducted to or from the first and second electric machines 56 and 72 for operation as motors or generators via transfer conductors 29 and 31 respectively.

FIG. 2 is a schematic block diagram of the distributed control module system. The elements described hereinafter comprise a subset of an overall vehicle control architecture, and provide coordinated system control of the exemplary hybrid powertrain described in FIG. 1. The distributed control module system synthesizes pertinent information and inputs, and executes algorithms to control various actuators to achieve control objectives, including objectives related to fuel economy, emissions, performance, drivability, and protection of hardware, including batteries of ESD 74 and the first and second electric machines 56 and 72. The distributed control module system includes an engine control module (hereafter ‘ECM’) 23, the TCM 17, a battery pack control module (hereafter ‘BPCM’) 21, a brake control module (hereafter ‘BrCM’) 22, and the TPIM 19. A hybrid control module (hereafter ‘HCP’) 5 provides supervisory control and coordination of the ECM 23, the TCM 17, the BPCM 21, the BrCM 22 and the TPIM 19. A user interface (‘UI’) 13 is operatively connected to a plurality of devices through which a vehicle operator controls or directs operation of the electro-mechanical hybrid powertrain. The devices include an accelerator pedal 113 (‘AP’) from which an operator torque request is determined, an operator brake pedal 112 (‘BP’), a transmission gear selector 114 (‘PRNDL’), and a vehicle speed cruise control (not shown). The transmission gear selector 114 may have a discrete number of operator-selectable positions, including the rotational direction of the output member 64 to enable one of a forward and a reverse direction.

The aforementioned control modules communicate with other control modules, sensors, and actuators via a local area network (hereafter ‘LAN’) bus 6. The LAN bus 6 allows for structured communication of states of operating parameters and actuator command signals between the various control modules. The specific communication protocol utilized is application-specific. The LAN bus 6 and appropriate protocols provide for robust messaging and multi-control module interfacing between the aforementioned control modules, and other control modules providing functionality including e.g., antilock braking, traction control, and vehicle stability. Multiple communications buses may be used to improve communications speed and provide some level of signal redundancy and integrity. Communication between individual control modules can also be effected using a direct link, e.g., a serial peripheral interface (‘SPI’) bus (not shown).

The HCP 5 provides supervisory control of the hybrid powertrain, serving to coordinate operation of the ECM 23, TCM 17, TPIM 19, and BPCM 21. Based upon various input signals from the user interface 13 and the hybrid powertrain, including the ESD 74, the HCP 5 determines various commands, including: the operator torque request, an output torque command (‘To_cmd’) to the driveline 90, an engine input torque command, clutch torque(s) (‘TCL’) for the torque-transfer clutches C1 70, C2 62, C3 73, C4 75 of the transmission 10; and the torque commands T_(A) and T_(B) for the first and second electric machines 56 and 72. The TCM 17 is operatively connected to the hydraulic control circuit 42 and provides various functions including monitoring various pressure sensing devices (not shown) and generating and communicating control signals to various solenoids (not shown) thereby controlling pressure switches and control valves contained within the hydraulic control circuit 42.

The ECM 23 is operatively connected to the engine 14, and functions to acquire data from sensors and control actuators of the engine 14 over a plurality of discrete lines, shown for simplicity as an aggregate bi-directional interface cable 35. The ECM 23 receives the engine input torque command from the HCP 5. The ECM 23 determines the actual engine input torque, T_(I), provided to the transmission 10 at that point in time based upon monitored engine speed and load, which is communicated to the HCP 5. The ECM 23 monitors input from the rotational speed sensor 11 to determine the engine input speed to the input shaft 12, which translates to the transmission input speed, N_(I). The ECM 23 monitors inputs from sensors (not shown) to determine states of other engine operating parameters including, e.g., a manifold pressure, engine coolant temperature, ambient air temperature, and ambient pressure. The engine load can be determined, for example, from the manifold pressure, or alternatively, from monitoring operator input to the accelerator pedal 113. The ECM 23 generates and communicates command signals to control engine actuators, including, e.g., fuel injectors, ignition modules, and throttle control modules, none of which are shown.

The TCM 17 is operatively connected to the transmission 10 and monitors inputs from sensors (not shown) to determine states of transmission operating parameters. The TCM 17 generates and communicates command signals to control the transmission 10, including controlling the hydraulic control circuit 42. Inputs from the TCM 17 to the HCP 5 include estimated clutch torques for each of the clutches, i.e., C1 70, C2 62, C3 73, and C4 75, and rotational output speed, N_(O), of the output member 64. Other actuators and sensors may be used to provide additional information from the TCM 17 to the HCP 5 for control purposes. The TCM 17 monitors inputs from pressure switches (not shown) and selectively actuates pressure control solenoids (not shown) and shift solenoids (not shown) of the hydraulic control circuit 42 to selectively actuate the various clutches C1 70, C2 62, C3 73, and C4 75 to achieve various transmission operating range states, as described hereinbelow.

The BPCM 21 is signally connected to sensors (not shown) to monitor the ESD 74, including states of electrical current and voltage parameters, to provide information indicative of parametric states of the batteries of the ESD 74 to the HCP 5. The parametric states of the batteries preferably include battery state-of-charge, battery voltage, battery temperature, and available battery power, referred to as a range P_(BAT) _(—) _(MIN) to P_(BAT) _(—) _(MAX).

A brake control module (hereafter ‘BrCM’) 22 is operatively connected to friction brakes (not shown) on each of the vehicle wheels 93. The BrCM 22 monitors the operator input to the brake pedal 112 and generates control signals to control the friction brakes and sends a control signal to the HCP 5 to operate the first and second electric machines 56 and 72 based thereon.

Each of the control modules ECM 23, TCM 17, TPIM 19, BPCM 21, and BrCM 22 is preferably a general-purpose digital computer comprising a microprocessor or central processing unit, storage mediums comprising read only memory (‘ROM’), random access memory (‘RAM’), electrically programmable read only memory (‘EPROM’), a high speed clock, analog to digital (‘A/D’) and digital to analog (‘D/A’) circuitry, and input/output circuitry and devices (‘I/O’) and appropriate signal conditioning and buffer circuitry. Each of the control modules has a set of control algorithms, comprising resident program instructions and calibrations stored in one of the storage mediums and executed to provide the respective functions of each computer. Information transfer between the control modules is preferably accomplished using the LAN bus 6 and SPI buses. The control algorithms are executed during preset loop cycles such that each algorithm is executed at least once each loop cycle. Algorithms stored in the non-volatile memory devices are executed by one of the central processing units to monitor inputs from the sensing devices and execute control and diagnostic routines to control operation of the actuators, using preset calibrations. Loop cycles are executed at regular intervals, for example each 3.125, 6.25, 12.5, 25 and 100 milliseconds during ongoing operation of the hybrid powertrain. Alternatively, algorithms may be executed in response to the occurrence of an event.

The exemplary hybrid powertrain selectively operates in one of several states that can be described in terms of engine states comprising one of an engine-on state (‘ON’) and an engine-off state (‘OFF’), and transmission operating range states comprising a plurality of fixed gears and continuously variable operating modes, described with reference to Table 1, below.

TABLE 1 Engine Transmission Operating Applied Description State Range State Clutches M1_Eng_Off OFF EVT Mode 1 C1 70 M1_Eng_On ON EVT Mode 1 C1 70 G1 ON Fixed Gear Ratio 1 C1 70 C4 75 G2 ON Fixed Gear Ratio 2 C1 70 C2 62 M2_Eng_Off OFF EVT Mode 2 C2 62 M2_Eng_On ON EVT Mode 2 C2 62 G3 ON Fixed Gear Ratio 3 C2 62 C4 75 G4 ON Fixed Gear Ratio 4 C2 62 C3 73 Neutral ON Neutral — —

Each of the transmission operating range states is described in the table and indicates which of the specific clutches C1 70, C2 62, C3 73, and C4 75 are applied for each of the operating range states. A first continuously variable mode, i.e., EVT Mode 1, or M1, is selected by applying clutch C1 70 only in order to “ground” the outer gear member of the third planetary gear set 28. The engine state can be one of ON (‘M1_Eng_On’) or OFF (‘M1_Eng_Off’). A second continuously variable mode, i.e., EVT Mode 2, or M2, is selected by applying clutch C2 62 only to connect the shaft 60 to the carrier of the third planetary gear set 28. The engine state can be one of ON (‘M2_Eng_On’) or OFF (‘M2_Eng_Off’). For purposes of this description, when the engine state is OFF, the engine input speed is equal to zero revolutions per minute (‘RPM’), i.e., the engine crankshaft is not rotating. A fixed gear operation provides a fixed ratio operation of input-to-output speed of the transmission 10, i.e., N_(I)/N_(O). A first fixed gear operation (‘G1’) is selected by applying clutches C1 70 and C4 75. A second fixed gear operation (‘G2’) is selected by applying clutches C1 70 and C2 62. A third fixed gear operation (‘G3’) is selected by applying clutches C2 62 and C4 75. A fourth fixed gear operation (‘G4’) is selected by applying clutches C2 62 and C3 73. The fixed ratio operation of input-to-output speed increases with increased fixed gear operation due to decreased gear ratios in the planetary gears 24, 26, and 28. The rotational speeds of the first and second electric machines 56 and 72, N_(A) and N_(B) respectively, are dependent on internal rotation of the mechanism as defined by the clutching and are proportional to the input speed measured at the input shaft 12.

In response to operator input via the accelerator pedal 113 and brake pedal 112 as captured by the user interface 13, the HCP 5 and one or more of the other control modules determine torque commands to control the torque actuators to meet the operator torque request at the output member 64 for transference to the driveline 90. The torque actuators preferably include torque generative devices, e.g., the engine 14 and torque machines comprising the first and second electric machines 56 and 72 in this embodiment. The torque actuators preferably further include a torque transferring device, comprising the transmission 10 in this embodiment. Based upon input signals from the user interface 13 and the hybrid powertrain including the ESD 74, the HCP 5 determines the operator torque request, a commanded output torque from the transmission 10 to the driveline 90, an input torque from the engine 14, clutch torques for the torque-transfer clutches C1 70, C2 62, C3 73, C4 75 of the transmission 10; and the motor torques for the first and second electric machines 56 and 72, respectively, as is described hereinbelow.

Final vehicle acceleration can be affected by other factors including, e.g., road load, road grade, and vehicle mass. The engine state and the transmission operating range state are determined based upon operating characteristics of the hybrid powertrain. This includes the operator torque request communicated through the accelerator pedal 113 and brake pedal 112 to the user interface 13 as previously described. The transmission operating range state and the engine state may be predicated on a hybrid powertrain torque demand caused by a command to operate the first and second electric machines 56 and 72 in an electrical energy generating mode or in a torque generating mode. The transmission operating range state and the engine state can be determined by an optimization algorithm or routine which determines optimum system efficiency based upon operator demand for power, battery state of charge, and energy efficiencies of the engine 14 and the first and second electric machines 56 and 72. The control system manages torque inputs from the engine 14 and the first and second electric machines 56 and 72 based upon an outcome of the executed optimization routine, and system efficiencies are optimized thereby, to manage fuel economy and battery charging. Furthermore, operation can be determined based upon a fault in a component or system. The HCP 5 monitors the torque-generative devices, and determines the power output from the transmission 10 at output member 64 that is required to meet the operator torque request while meeting other powertrain operating demands, e.g., charging the ESD 74. As should be apparent from the description above, the ESD 74 and the first and second electric machines 56 and 72 are electrically-operatively coupled for power flow therebetween. Furthermore, the engine 14, the first and second electric machines 56 and 72, and the electro-mechanical transmission 10 are mechanically-operatively coupled to transfer power therebetween to generate a power flow to the output member 64.

FIG. 3 shows a control system architecture for controlling and managing signal flow in a hybrid powertrain system having multiple torque generative devices, described hereinbelow with reference to the hybrid powertrain system of FIGS. 1 and 2, and residing in the aforementioned control modules in the form of executable algorithms and calibrations. The control system architecture is applicable to alternative hybrid powertrain systems having multiple torque generative devices, including, e.g., a hybrid powertrain system having an engine and a single electric machine, a hybrid powertrain system having an engine and multiple electric machines. Alternatively, the hybrid powertrain system can utilize non-electric torque machines and energy storage systems, e.g., hydraulic-mechanical hybrid transmissions using hydraulically powered torque machines (not shown).

In operation, the operator inputs to the accelerator pedal 113 and the brake pedal 112 are monitored to determine the operator torque request. The operator inputs to the accelerator pedal 113 and the brake pedal 112 comprise individually determinable operator torque request inputs including an immediate accelerator output torque request (‘Output Torque Request Accel Immed’), a predicted accelerator output torque request (‘Output Torque Request Accel Prdtd’), an immediate brake output torque request (‘Output Torque Request Brake Immed’), a predicted brake output torque request (‘Output Torque Request Brake Prdtd’) and an axle torque response type (‘Axle Torque Response Type’). As used herein, the term ‘accelerator’ refers to an operator request for forward propulsion preferably resulting in increasing vehicle speed over the present vehicle speed, when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the forward direction. The terms ‘deceleration’ and ‘brake’ refer to an operator request preferably resulting in decreasing vehicle speed from the present vehicle speed. The immediate accelerator output torque request, the predicted accelerator output torque request, the immediate brake output torque request, the predicted brake output torque request, and the axle torque response type are individual inputs to the control system. Additionally, operation of the engine 14 and the transmission 10 are monitored to determine the input speed (‘Ni’) and the output speed (‘No’).

The immediate accelerator output torque request comprises an immediate torque request determined based upon the operator input to the accelerator pedal 113. The control system controls the output torque from the hybrid powertrain system in response to the immediate accelerator output torque request to cause positive acceleration of the vehicle. The immediate brake output torque request comprises an immediate braking request determined based upon the operator input to the brake pedal 112. The control system controls the output torque from the hybrid powertrain system in response to the immediate brake output torque request to cause deceleration, or negative acceleration, of the vehicle. Vehicle deceleration effected by control of the output torque from the hybrid powertrain system is combined with vehicle deceleration effected by a vehicle braking system (not shown) to decelerate the vehicle to achieve the immediate braking request.

The immediate accelerator output torque request is determined based upon a presently occurring operator input to the accelerator pedal 113, and comprises a request to generate an immediate output torque at the output member 64 preferably to accelerate the vehicle. The immediate accelerator output torque request is unshaped, but can be shaped by events that affect vehicle operation outside the powertrain control. Such events include vehicle level interruptions in the powertrain control for antilock braking, traction control and vehicle stability control, which can be used to unshape or rate-limit the immediate accelerator output torque request.

The predicted accelerator output torque request is determined based upon the operator input to the accelerator pedal 113 and comprises an optimum or preferred output torque at the output member 64. The predicted accelerator output torque request is preferably equal to the immediate accelerator output torque request during normal operating conditions, e.g., when any one of antilock braking, traction control, or vehicle stability is not being commanded. When any one of antilock braking, traction control or vehicle stability is being commanded the predicted accelerator output torque request remains the preferred output torque with the immediate accelerator output torque request being decreased in response to output torque commands related to the antilock braking, traction control, or vehicle stability control.

The immediate brake output torque request is determined based upon the operator input to the brake pedal 112 and the control signal to control the friction brakes to generate friction braking torque.

The predicted brake output torque request comprises an optimum or preferred brake output torque at the output member 64 in response to an operator input to the brake pedal 112 subject to a maximum brake output torque generated at the output member 64 allowable regardless of the operator input to the brake pedal 112. In one embodiment the maximum brake output torque generated at the output member 64 is limited to −0.2 g. The predicted brake output torque request can be phased out to zero when vehicle speed approaches zero regardless of the operator input to the brake pedal 112. As desired by a user, there can be operating conditions under which the predicted brake output torque request is set to zero, e.g., when the operator setting to the transmission gear selector 114 is set to a reverse gear, and when a transfer case (not shown) is set to a four-wheel drive low range. The operating conditions whereat the predicted brake output torque request is set to zero are those in which blended braking is not preferred due to vehicle operating factors.

The axle torque response type comprises an input state for shaping and rate-limiting the output torque response through the first and second electric machines 56 and 72. The input state for the axle torque response type can be an active state, preferably comprising one of a pleasability limited state a maximum range state, and an inactive state. When the commanded axle torque response type is the active state, the output torque command is the immediate output torque. Preferably the torque response for this response type is as fast as possible.

Blended brake torque includes a combination of the friction braking torque generated at the wheels 93 and the output torque generated at the output member 64 which reacts with the driveline 90 to decelerate the vehicle in response to the operator input to the brake pedal 112. The BrCM 22 commands the friction brakes on the wheels 93 to apply braking force and generates a command for the transmission 10 to create a negative output torque which reacts with the driveline 90 in response to the immediate braking request. Preferably the applied braking force and the negative output torque can decelerate and stop the vehicle so long as they are sufficient to overcome vehicle kinetic power at wheel(s) 93. The negative output torque reacts with the driveline 90, thus transferring torque to the electro-mechanical transmission 10 and the engine 14. The negative output torque reacted through the electro-mechanical transmission 10 can be transferred to the first and second electric machines 56 and 72 to generate electric power for storage in the ESD 74.

A strategic optimization control scheme (‘Strategic Control’) 310 determines a preferred input speed (‘Ni_Des’) and a preferred engine state and transmission operating range state (‘Hybrid Range State Des’) based upon the output speed and the operator torque request and based upon other operating parameters of the hybrid powertrain, including battery power limits and response limits of the engine 14, the transmission 10, and the first and second electric machines 56 and 72. The predicted accelerator output torque request and the predicted brake output torque request are input to the strategic optimization control scheme 310. The strategic optimization control scheme 310 is preferably executed by the HCP 5 during each 100 ms loop cycle and each 25 ms loop cycle. The desired operating range state for the transmission 10 and the desired input speed from the engine 14 to the transmission 10 are inputs to the shift execution and engine start/stop control scheme 320.

The shift execution and engine start/stop control scheme 320 commands changes in the transmission operation (‘Transmission Commands’) including changing the operating range state based upon the inputs and operation of the powertrain system. This includes commanding execution of a change in the transmission operating range state if the preferred operating range state is different from the present operating range state by commanding changes in application of one or more of the clutches C1 70, C2 62, C3 73, and C4 75 and other transmission commands. The present operating range state (‘Hybrid Range State Actual’) and an input speed profile (‘Ni_Prof’) can be determined. The input speed profile is an estimate of an upcoming input speed and preferably comprises a scalar parametric value that is a targeted input speed for the forthcoming loop cycle.

A tactical control scheme (‘Tactical Control and Operation’) 330 is repeatedly executed during one of the control loop cycles to determine engine commands (‘Engine Commands’) for operating the engine 14, including a preferred input torque from the engine 14 to the transmission 10 based upon the output speed, the input speed, and the operator torque request comprising the immediate accelerator output torque request, the predicted accelerator output torque request, the immediate brake output torque request, the predicted brake output torque request, the axle torque response type, and the present operating range state for the transmission. The engine commands also include engine states including one of an all-cylinder operating state and a cylinder deactivation operating state wherein a portion of the engine cylinders are deactivated and unfueled, and engine states including one of a fueled state and a fuel cutoff state. An engine command comprising the preferred input torque of the engine 14 and a present input torque (‘Ti’) reacting between the engine 14 and the input member 12 are preferably determined in the ECM 23. Clutch torques (‘Tcl’) for each of the clutches C1 70, C2 62, C3 73, and C4 75, including the presently applied clutches and the non-applied clutches are estimated, preferably in the TCM 17.

An output and motor torque determination scheme (‘Output and Motor Torque Determination’) 340 is executed to determine the preferred output torque from the powertrain (‘To_cmd’). This includes determining motor torque commands (‘T_(A)’, ‘T_(B)’) to transfer a net commanded output torque to the output member 64 of the transmission 10 that meets the operator torque request, by controlling the first and second electric machines 56 and 72 in this embodiment. The immediate accelerator output torque request, the immediate brake output torque request, the present input torque from the engine 14 and the estimated applied clutch torque(s), the present operating range state of the transmission 10, the input speed, the input speed profile, and the axle torque response type are inputs. The output and motor torque determination scheme 340 executes to determine the motor torque commands during each iteration of one of the loop cycles. The output and motor torque determination scheme 340 includes algorithmic code which is regularly executed during the 6.25 ms and 12.5 ms loop cycles to determine the preferred motor torque commands.

The hybrid powertrain is controlled to transfer the output torque to the output member 64 to react with the driveline 90 to generate tractive torque at wheel(s) 93 to forwardly propel the vehicle in response to the operator input to the accelerator pedal 113 when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the forward direction. Similarly, the hybrid powertrain is controlled to transfer the output torque to the output member 64 to react with the driveline 90 to generate tractive torque at wheel(s) 93 to propel the vehicle in a reverse direction in response to the operator input to the accelerator pedal 113 when the operator selected position of the transmission gear selector 114 commands operation of the vehicle in the reverse direction. Preferably, propelling the vehicle results in vehicle acceleration so long as the output torque is sufficient to overcome external loads on the vehicle, e.g., due to road grade, aerodynamic loads, and other loads.

FIG. 4 details signal flow for the output and motor torque determination scheme 340 for controlling and managing the output torque through the first and second electric machines 56 and 72, described with reference to the hybrid powertrain system of FIGS. 1 and 2 and the control system architecture of FIG. 3. The output and motor torque determination scheme 340 controls the motor torque commands of the first and second electric machines 56 and 72 to transfer a net output torque to the output member 64 of the transmission 10 that reacts with the driveline 90 and meets the operator torque request, subject to constraints and shaping. The output and motor torque determination scheme 340 preferably includes algorithmic code and predetermined calibration code which is regularly executed during the 6.25 ms and 12.5 ms loop cycles to determine preferred motor torque commands (‘T_(A)’, ‘T_(B)’) for controlling the first and second electric machines 56 and 72 in this embodiment.

The output and motor torque determination scheme 340 determines and uses a plurality of inputs to determine constraints on the output torque, from which it determines the output torque command (‘To_cmd’). The motor torque commands (‘T_(A)’, ‘T_(B)’) for the first and second electric machines 56 and 72 can be determined based upon the output torque command. The inputs to the output and motor torque determination scheme 340 include operator inputs, powertrain system inputs and constraints, and autonomic control inputs.

The operator inputs include the immediate accelerator output torque request (‘Output Torque Request Accel Immed’) and the immediate brake output torque request (‘Output Torque Request Brake Immed’).

The autonomic control inputs include torque offsets to effect active damping of the driveline 90 (412), to effect engine pulse cancellation (408), and to effect a closed loop correction based upon the input and clutch slip speeds (410). The torque offsets for the first and second electric machines 56 and 72 to effect active damping of the driveline 90 can be determined (‘Ta AD’, ‘Tb AD’), e.g., to manage and effect driveline lash adjustment, and are output from an active damping algorithm (‘AD’) (412). The torque offsets to effect engine pulse cancellation (‘Ta PC’, ‘Tb PC’) are determined during starting and stopping of the engine during transitions between the engine-on state (‘ON’) and the engine-off state (‘OFF’) to cancel engine torque disturbances, and are output from a pulse cancellation algorithm (‘PC’) (408). The torque offsets for the first and second electric machines 56 and 72 to effect closed-loop correction torque are determined by monitoring input speed to the transmission 10 and clutch slip speeds of clutches C1 70, C2 62, C3 73, and C4 75. The closed-loop correction torque offsets for the first and second electric machines 56 and 72 (‘Ta CL’, ‘Tb CL’) can be determined based upon an input speed error, i.e., a difference between the input speed from sensor 11 (‘Ni’) and the input speed profile (‘Ni_Prof’) and a clutch slip speed error, i.e., a difference between clutch slip speed and a targeted clutch slip speed, e.g., a clutch slip speed profile for a targeted clutch C1 70. When operating in one of the mode operating range states, the closed-loop correction torque offsets for the first and second electric machines 56 and 72 (‘Ta CL’, ‘Tb CL’) can be determined primarily based upon the input speed error. When operating in Neutral, the closed-loop correction is based upon the input speed error and the clutch slip speed error for a targeted clutch, e.g., C1 70. The closed-loop correction torque offsets are output from a closed loop control algorithm (‘CL’) (410). The clutch slip speeds of the non-applied clutches can be determined for the specific operating range state based upon motor speeds for the first and second electric machines 56 and 72 and the speed of the output member 64. The targeted clutch slip speed and clutch slip profile are preferably used during a transition in the operating range state of the transmission to synchronize clutch slip speed prior to applying an oncoming clutch. The closed-loop motor torque offsets and the motor torque offsets to effect active damping of the driveline 90 are input to a low pass filter (‘LPF’) 405 to determine filtered motor torque corrections for the first and second electric machines 56 and 72 (‘Ta LPF’ and Tb LPF’).

The powertrain system inputs and constraints include maximum and minimum available battery power limits (‘P_(BAT) Min/Max’) output from a battery power limit algorithm (‘P BAT’) (466), the operating range state (‘Hybrid Range State’), and a plurality of system inputs and constraints (‘System Inputs and Constraints’). The system inputs can include scalar parameters specific to the powertrain system and the operating range state, and can be related to speed and acceleration of the input member 12, output member 64, and the clutches. Other system inputs are related to system inertias, damping, and electric/mechanical power conversion efficiencies in this embodiment. The constraints include maximum and minimum motor torque outputs from the torque machines, i.e., first and second electric machines 56 and 72 and maximum and minimum clutch reactive torques for the applied clutches. Other system inputs include the input torque, clutch slip speeds and other relevant states.

Inputs including an input acceleration profile (‘Nidot_Prof’) and a clutch slip acceleration profile (“Clutch Slip Accel Prof”) are input to a pre-optimization algorithm (415), along with the system inputs, the operating range state, and the motor torque corrections for the first and second electric machines 56 and 72 (‘Ta LPF’ and Tb LPF’). The input acceleration profile is an estimate of an upcoming input acceleration that preferably comprises a targeted input acceleration for the forthcoming loop cycle. The clutch slip acceleration profile is an estimate of upcoming clutch acceleration for one or more of the non-applied clutches, and preferably comprises a targeted clutch slip acceleration for the forthcoming loop cycle. Optimization inputs (‘Opt Inputs’), which can include values for motor torques, clutch torques and output torques can be calculated for the present operating range state and used in an optimization algorithm (440). The optimization algorithm (440) is preferably executed to determine the maximum and minimum raw output torque constraints (440) and to determine the preferred split of open-loop torque commands between the first and second electric machines 56 and 72 (440′). The optimization inputs, the maximum and minimum battery power limits, the system inputs and the present operating range state are analyzed to determine a preferred or optimum output torque (‘To Opt’) and minimum and maximum raw output torque constraints (‘To Min Raw’, ‘To Max Raw’) which can be shaped and filtered (420). The preferred output torque (‘To Opt’) comprises an output torque that minimizes battery power subject to a range of net output torques that are less than the immediate accelerator output torque request. The preferred output torque comprises the net output torque that is less than the immediate accelerator output torque request and yields the minimum battery power subject to the output torque constraints. The immediate accelerator output torque request and the immediate brake output torque request are each shaped and filtered and subjected to the minimum and maximum output torque constraints (‘To Min Filt’, ‘To Max Filt’) to determine minimum and maximum filtered output torque request constraints (‘To Min Req Filt’, ‘To Max Req Filt’). A constrained accelerator output torque request (‘To Req Accel Cnstrnd’) and a constrained brake output torque request (‘To Req Brake Cnstrnd’) can be determined based upon the minimum and maximum filtered output torque request constraints (425).

Furthermore, a regenerative braking capacity (‘Opt Regen Capacity’) of the transmission 10 comprises a capacity of the transmission 10 to react driveline torque, and can be determined based upon constraints including maximum and minimum motor torque outputs from the torque machines and maximum and minimum reactive torques for the applied clutches, taking into account the battery power limits. The regenerative braking capacity establishes a maximum value for the immediate brake output torque request. The regenerative braking capacity is determined based upon a difference between the constrained accelerator output torque request and the preferred output torque (‘To Opt’). The constrained accelerator output torque request is shaped and filtered and combined with a constrained, shaped, and filtered brake output torque request to determine a net output torque command. The net output torque command is compared to the minimum and maximum request filtered output torques to determine the output torque command (‘To_cmd’) (430). When the net output torque command is between the maximum and minimum request filtered output torques, the output torque command is set to the net output torque command. When the net output torque command exceeds the maximum request filtered output torque, the output torque command is set to the maximum request filtered output torque. When the net output torque command is less than the minimum request filtered output torque, the output torque command is set to the minimum request filtered output torque command.

Powertrain operation is monitored and combined with the output torque command to determine a preferred split of open-loop torque commands between the first and second electric machines 56 and 72 that meets reactive clutch torque capacities (‘Ta Opt’ and ‘Tb Opt’), and provide feedback related to the preferred battery power (‘Pbat Opt’) (440′). The motor torque corrections for the first and second electric machines 56 and 72 (‘Ta LPF’ and Tb LPF’) are subtracted to determine open loop motor torque commands (‘Ta OL’ and ‘Tb OL’) (460).

The open loop motor torque commands are combined with the autonomic control inputs including the torque offsets to effect active damping of the driveline 90 (412), to effect engine pulse cancellation (408), and to effect a closed loop correction based upon the input and clutch slip speeds (410), to determine the motor torques T_(A) and T_(B) for controlling the first and second electric machines 56 and 72 (470). The aforementioned steps of constraining, shaping and filtering the output torque request to determine the output torque command which is converted into the torque commands for the first and second electric machines 56 and 72 is preferably a feed-forward operation which acts upon the inputs and uses algorithmic code to calculate the torque commands.

The system operation as configured leads to determining output torque constraints based upon present operation and constraints of the powertrain system. The operator torque request is determined based upon operator inputs to the brake pedal and to the accelerator pedal. The operator torque request can be constrained, shaped and filtered to determine the output torque command, including determining a preferred regenerative braking capacity. An output torque command can be determined that is constrained based upon the constraints and the operator torque request. The output torque command is implemented by commanding operation of the torque machines. The system operation effects powertrain operation that is responsive to the operator torque request and within system constraints. The system operation results in an output torque shaped with reference to operator driveability demands, including smooth operation during regenerative braking operation.

The optimization algorithm (440, 440′) comprises an algorithm executed to determine powertrain system control parameters that are responsive to the operator torque request that minimizes battery power consumption. The optimization algorithm (440, 440′) includes monitoring present operating conditions of the electro-mechanical hybrid powertrain, e.g., the powertrain system described hereinabove, based upon the system inputs and constraints, the present operating range state, and the available battery power limits. For a candidate input torque, the optimization algorithm (440, 440′) calculates powertrain system outputs that are responsive to the system inputs comprising the aforementioned output torque commands and are within the maximum and minimum motor torque outputs from the first and second electric machines 56 and 72, and within the available battery power, and within the range of clutch reactive torques from the applied clutches for the present operating range state of the transmission 10, and take into account the system inertias, damping, clutch slippages, and electric/mechanical power conversion efficiencies. Preferably, the powertrain system outputs include the preferred output torque (‘To Opt’), achievable torque outputs from the first and second electric machines 56 and 72 (‘Ta Opt’, ‘Tb Opt’) and the preferred battery power (‘Pbat Opt’) associated with the achievable torque outputs.

FIGS. 5, 6, and 7 show the optimization algorithm (440, 440′), which includes monitoring present operating conditions of the electro-mechanical hybrid powertrain, e.g., the powertrain system described hereinabove. Offset motor torques for the first and second electric machines 56 and 72 can be calculated based upon inputs including the operating range state (‘ORS’) of the transmission 10, the input torque (‘T_(I)’) and other terms based upon system inertias, system damping, and clutch slippage (510).

FIG. 6 graphically shows an operating region for an exemplary powertrain system, including determining linear torque constraints to the output torque (520) to determine a region of allowable motor torques for the first and second electric machines 56 and 72 in this embodiment. The graph in FIG. 6 shows motor torque constraints (‘Motor Torque Constraints’) comprising minimum and maximum achievable motor torques for the first and second electric machines 56 and 72, and depicted in FIG. 5 (‘T_(A)Min’, ‘T_(A)Max’, ‘T_(B)Min’, and ‘T_(B)Max’). Minimum and maximum clutch reactive torques for applied clutch(es) CL1 and CL2 are graphed relative to the motor torque constraints, for first and, as shown (where necessary), second applied clutches (‘T_(CL1) MIN’, ‘T_(CL1) MAX’) and (‘T_(CL2) MIN’, ‘T_(CL2) MAX’), also depicted in FIG. 5 (‘T_(CLn)Min’, ‘T_(CLn)Max’). Minimum and maximum linear output torques (‘To Min Lin’, ‘To Max Lin’) can be determined based upon the offset motor torques, the minimum and maximum achievable motor torques for the first and second electric machines 56 and 72 and the minimum and maximum clutch reactive torques for the applied clutch(es). The minimum and maximum linear output torques are the minimum and maximum output torques that meet the motor torque constraints and also meet the applied clutch torque constraints. In the example shown, the minimum and maximum clutch reactive torques for the second applied clutch CL2 are less restrictive and outside the motor torque constraints, and thus do not constrain the output torque. Operation is bounded by the region defined by the minimum and maximum clutch reactive torques for the first applied clutch CL1 and the minimum and maximum motor torque constraints for the second electric machine 72 (‘T_(B)Min’ and ‘T_(B)Max’). The maximum linear output torque is the maximum output torque in this region, i.e., the output torque at the intersection between the maximum motor torque constraint for the second electric machine 72 (‘T_(B)Max’) and minimum clutch reactive torque for the first applied clutch (‘T_(CL1) Min’). The minimum linear output torque is the minimum output torque in this region, i.e., the output torque at the intersection between the minimum motor torque command for the second electric machine 72 (‘Tb Min’) and maximum clutch reactive torque for the first applied clutch (‘T_(CL1) Max’).

FIG. 7 graphically shows battery power (P_(BAT)) plotted against output torque (‘T_(O)’) having a (0, 0) point designated by letter M, for an exemplary system. The graph as depicted can be used to determine an unconstrained quadratic solution, which includes an optimized output torque (‘To*’) and an optimized battery power (‘P_(BAT)*’) for operating the system with no other system constraints (530). The power for the energy storage device 74 can be represented mathematically as a function of the transmission output torque To as shown below: P _(BAT)(T _(O))=(a ₁ ² +b ₁ ²)(T _(O) −T _(O)*)² +P _(BAT)*  [1] where a₁ and b₁ represent scalar values determined for the specific application. Eq. 1 can be solved for the output torque, as shown below.

$\begin{matrix} {{T_{O}\left( P_{BAT} \right)} = {T_{O}^{*} \pm \sqrt{\frac{P_{BAT} - P_{BAT}^{*}}{a_{1}^{2} + b_{1}^{2}}}}} & \lbrack 2\rbrack \end{matrix}$

For the available battery power range P_(BAT) _(—) _(MIN) to P_(BAT) _(—) _(MAX), four distinct output torques can be determined from Eq. 2, including maximum and minimum quadratic output torque constraints for the positive root case (‘To@P_(BAT)Max Pos’ and ‘To@P_(BAT)Min Pos’), and minimum and maximum quadratic output torque constraints for the negative root case (‘To@P_(BAT)Max Neg’ and ‘To@P_(BAT)Min Neg’), plotted with reference to FIG. 7. FIG. 7 shows valid, achievable ranges for the output torque based upon the battery power.

The preferred output torque (‘To Opt’) can be determined based upon the optimized output torque (‘To*’), the optimized battery power (‘P_(BAT)*’), the maximum and minimum linear torque output, and the output torque search range (‘To Search Range’). The output torque search range (‘To Search Range’) preferably comprises the immediate accelerator output torque request when the optimization algorithm is executed to determine the maximum and minimum raw output torque constraints (440). This includes selecting a temporary output torque comprising a minimum torque value of the search range for the output torque and the maximum output torque. The output torque search range (‘To Search Range’) preferably comprises the output torque command (‘To_cmd’) when the optimization algorithm is used to determine the preferred split of open-loop torque commands between the first and second electric machines 56 and 72 (440′).

The preferred output torque (‘To Opt’) is selected as the maximum of the temporary output torque, the minimum output torque determined based upon one of the quadratic output torque constraints and clutch torque constraints, and the minimum linear output torque (540). Output torque constraints including minimum and maximum unfiltered output torques (‘To Min Raw’, ‘To Max Raw’) are determined based upon inputs including a capability of the powertrain to transmit and convert electric power to mechanical torque through the first and second electric machines 56 and 72 (‘Ta Min/Max’, ‘Tb Min/Max’) and the immediate or present torque, speed, and electric power inputs thereto. The preferred output torque (‘To Opt’) is determined based upon inputs including the immediate accelerator output torque request.

The preferred output torque (‘To Opt’) is subject to output torque constraints comprising the minimum and maximum unfiltered output torques (‘To Min Raw’, ‘To Max Raw’) and is determined based upon the range of allowable output torques, which can vary, and may include the immediate accelerator output torque request. The preferred output torque may comprise an output torque corresponding to a minimum battery discharge power or an output torque corresponding to a maximum battery charge power. The preferred output torque is based upon a capacity of the powertrain to transmit and convert electric power to mechanical torque through the first and second electric machines 56 and 72, and the immediate or present torque, speed, and reactive clutch torque constraints, and electric power inputs thereto. The output torque constraints including the minimum and maximum unfiltered output torques (‘To Min Raw’, ‘To Max Raw’) and the preferred output torque (‘To Opt’) can be determined by executing and solving an optimization function in one of the operating range states for neutral, mode and fixed gear operation. The optimization function 440 comprises a plurality of linear equations implemented in an executable algorithm and solved during ongoing operation of the system to determine the preferred output torque range to minimize battery power consumption and meet the operator torque request. Each of the linear equations takes into account the input torque (‘Ti’), system inertias and linear damping. Preferably, there are linear equations specific to each of the operating range states for neutral, mode and fixed gear operations, described with reference to Eqs. 3-10, below.

The output torque constraints comprise a preferred output torque range at the present input torque, within the available battery power (‘P_(BAT) Min/Max’) and within the motor torque constraints subject to the reactive clutch torques of the applied torque transfer clutches. The output torque request is constrained within maximum and minimum output torque capacities. In fixed gear and mode operation, the preferred output torque can comprise the output torque which maximizes charging of the ESD 74. In neutral, the preferred output torque is calculated. In fixed gear operation, the preferred output torque can include the preferred torque split between the first and second electric machines 56 and 72 while meeting the reactive clutch torque constraints.

Preferred motor torques and battery powers (‘T_(A) Opt’, ‘T_(B) Opt’, and ‘P_(BAT) Opt’) can be determined based upon the preferred output torque, and used to control operation of the powertrain system. The preferred motor torques comprise motor torques which minimize power flow from the ESD 74 and achieve the preferred output torque. Torque outputs from the first and second electric machines 56 and 72 are controlled based upon the determined minimum power flow from the battery, which is the preferred battery power (‘P_(BAT) Opt’). Torque output is controlled based upon the engine input torque and the torque commands for the first and second electric machines 56 and 72, (‘T_(A) Opt’, ‘T_(B) Opt’) respectively, which minimizes the power flow from the ESD 74 to meet the preferred output torque. The battery powers associated with the motors (‘P_(A) Opt’ and ‘P_(B) Opt’, respectively) can be determined based upon the torque commands (560). Linear equations for the operating range states for neutral, mode and fixed gear operations are now described. When the transmission 14 is in the neutral operating range state the linear equation system is Eq. 3 as set forth below:

$\begin{matrix} {\begin{bmatrix} T_{A} \\ T_{B} \\ T_{O} \end{bmatrix} = {{\begin{bmatrix} {a\; 1} \\ {a\; 2} \\ {a\; 3} \end{bmatrix}T_{I}} + {\quad{{\left\lbrack \begin{matrix} {a\; 11} & {a\; 12} & {a\; 13} \\ {a\; 21} & {a\; 22} & {a\; 23} \\ {a\; 31} & {a\; 32} & {a\; 33} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} {Nidot} \\ {Nodot} \\ {Ncdot} \end{matrix} \right\rbrack} + {\left\lbrack \begin{matrix} {b\; 11} & {b\; 12} & {b\; 13} \\ {b\; 21} & {b\; 22} & {b\; 23} \\ {b\; 31} & {b\; 32} & {b\; 33} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} N_{I} \\ N_{O} \\ N_{C} \end{matrix} \right\rbrack} + {\quad{\left\lbrack \begin{matrix} {c\; 11} & {c\; 12} & {c\; 13} & {c\; 14} \\ {c\; 21} & {c\; 22} & {c\; 23} & {c\; 24} \\ {c\; 31} & {c\; 32} & {c\; 33} & {c\; 34} \\ {c\; 41} & {c\; 41} & {c\; 43} & {c\; 44} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \\ {{Tcs}\; 3} \\ {{Tcs}\; 4} \end{matrix} \right\rbrack}}}}}} & \lbrack 3\rbrack \end{matrix}$

The term

$\begin{bmatrix} {a\; 1} \\ {a\; 2} \\ {a\; 3} \end{bmatrix}T_{I}$ represents contributions to the motor torques (T_(A), T_(B)) and the output torque (T_(O)) due to the input torque. The ta2 and a3 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {a\; 11} & {a\; 12} & {a\; 13} \\ {a\; 21} & {a\; 22} & {a\; 23} \\ {a\; 31} & {a\; 32} & {a\; 33} \end{bmatrix}*\begin{bmatrix} {Nidot} \\ {Nodot} \\ {Ncdot} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the output torque (T_(O)) due to system inertias, having three degrees of freedom.

The term

$\begin{bmatrix} {b\; 11} & {b\; 12} & {b\; 13} \\ {b\; 21} & {b\; 22} & {b\; 23} \\ {b\; 31} & {b\; 32} & {b\; 33} \end{bmatrix}*\begin{bmatrix} N_{I} \\ N_{O} \\ N_{C} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the output torque (T_(O)) due to linear damping, having three degrees of freedom. The Ni, No and Nc terms are selected as three linearly independent system speeds, comprising the input speed, the output speed, and clutch slip speed, which can be used to characterize the damping of the components of the powertrain system. And the b11-b33 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {c\; 11} & {c\; 12} & {c\; 13} & {c\; 14} \\ {c\; 21} & {c\; 22} & {c\; 23} & {c\; 24} \\ {c\; 31} & {c\; 32} & {c\; 33} & {c\; 34} \\ {c\; 41} & {c\; 41} & {c\; 43} & {c\; 44} \end{bmatrix}*\begin{bmatrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \\ {{Tcs}\; 3} \\ {{Tcs}\; 4} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the output torque (T_(O)) due to slipping clutch torques. The Tcs1, Tcs2, Tcs3, and Tcs4 terms represent the slipping clutch torques across the respective torque transfer clutches, i.e., clutches C1 70, C2 62, C3 73, and C4 75. And, the c11-c44 terms are system-specific scalar values determined for the specific system application. One skilled in the art can readily see application of this concept to any number of slipping clutches.

The input acceleration term, the output acceleration term, and the clutch acceleration term are selected as three linearly independent system accelerations which can be used to characterize the inertias of the components of the powertrain system. The a11-a33 terms are system-specific scalar values determined for the specific system application.

When the transmission 14 is in one of the mode operating range states the linear equation for the system is Eq. 4:

$\begin{matrix} {\begin{bmatrix} T_{A} \\ T_{B} \\ T_{{CL}\; 1} \end{bmatrix} = {{\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{O}} \\ k_{T_{B}{From}\mspace{11mu} T_{O}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{O}} \end{bmatrix}T_{O}} + {\quad{{\left\lbrack \begin{matrix} k_{T_{A}{From}\mspace{11mu} T_{I}} \\ k_{T_{B}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \end{matrix} \right\rbrack T_{I}} + {\left\lbrack \begin{matrix} {a\; 11} & {a\; 12} \\ {a\; 21} & {a\; 22} \\ {a\; 31} & {a\; 32} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} {Nidot} \\ {Nodot} \end{matrix} \right\rbrack} + {\quad{{\left\lbrack \begin{matrix} {b\; 11} & {b\; 12} \\ {b\; 21} & {b\; 22} \\ {b\; 31} & {b\; 32} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} N_{I} \\ N_{O} \end{matrix} \right\rbrack} + {\left\lbrack \begin{matrix} {c\; 11} & {c\; 12} & {c\; 13} \\ {c\; 21} & {c\; 22} & {c\; 23} \\ {c\; 31} & {c\; 32} & {c\; 33} \end{matrix} \right\rbrack*\begin{bmatrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \\ {{Tcs}\; 3} \end{bmatrix}}}}}}}} & \lbrack 4\rbrack \end{matrix}$

Eq. 4 can be solved to determine a preferred output torque which minimizes the battery power and meets the operator torque request. The T_(CL1) term represents reactive torque transfer across the applied clutch for the mode operation, i.e., clutch C1 62 in Mode 1 and clutch C2 70 in Mode 2. The terms Tcs1, Tcs2, Tcs3 represent torque transfer across the non-applied, slipping clutches for the specific mode operation.

The term

$\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{I}} \\ k_{T_{B}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \end{bmatrix}T_{I}$ represents contributions to the motor torques (T_(A), T_(B)) and the reactive torque transfer across the applied clutch T_(CL1) due to the input torque T_(I). The scalar terms are based upon the torque outputs from the first and second electric machines 56 and 72 and the reactive torque of the applied clutch related to the input torque (‘k_(TA from TI)’, ‘k_(TB from TI)’, ‘k_(TCL1 from TI)’) determined for the specific system application.

The term

$\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{O}} \\ k_{T_{B}{From}\mspace{11mu} T_{O}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{O}} \end{bmatrix}T_{O}$ represents contributions to the motor torques (T_(A), T_(B)) and the reactive torque transfer across the applied clutch T_(CL1) due to the output torque T_(O). The scalar terms are based upon the torque outputs from the first and second electric machines 56 and 72 and the reactive torque of the applied clutch related to the input torque (‘k_(TA from To)’, ‘k_(TB from To)’, ‘k_(TCL1 from To)’) determined for the specific system application.

The term

$\begin{bmatrix} {a\; 11} & {a\; 12} \\ {a\; 21} & {a\; 22} \\ {a\; 31} & {a\; 32} \end{bmatrix}*\begin{bmatrix} {Nidot} \\ {Nodot} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the reactive torque transfer across the applied clutch T_(CL1) due to system inertias, having two degrees of freedom. The input acceleration term and the output acceleration term are selected as two linearly independent system accelerations which can be used to characterize the inertias of the components of the powertrain system. The a11-a32 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {b\; 11} & {b\; 12} \\ {b\; 21} & {b\; 22} \\ {b\; 31} & {b\; 32} \end{bmatrix}*\begin{bmatrix} N_{I} \\ N_{O} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the reactive torque transfer across the applied clutch T_(CL1) due to linear damping, having two degrees of freedom, selected as two linearly independent system speeds, i.e., the input and output speeds, which can be used to characterize the damping of the components of the powertrain system. The b11-b32 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {c\; 11} & {c\; 12} & {c\; 13} \\ {c\; 21} & {c\; 22} & {c\; 23} \\ {c\; 31} & {c\; 32} & {c\; 33} \end{bmatrix}*\begin{bmatrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \\ {{Tcs}\; 3} \end{bmatrix}$ represents contributions to the motor torques (T_(A), T_(B)) and the reactive torque transfer across the applied clutch T_(CL1) due to non-applied, slipping clutch torques. The Tcs1, Tcs2, and Tcs3 terms represent clutch torques across the non-applied, slipping torque transfer clutches. The c11-c33 terms are system-specific scalar values determined for the specific system application.

Eq. 4 can be rewritten as Eq. 5:

$\begin{matrix} {\begin{bmatrix} T_{A} \\ T_{B} \\ T_{{CL}\; 1} \end{bmatrix} = {{\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{O}} \\ k_{T_{B}{From}\mspace{11mu} T_{O}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{O}} \end{bmatrix}T_{O}} + {\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{I}} \\ k_{T_{B}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \end{bmatrix}T_{I}} + \begin{bmatrix} {T_{A}{Misc}} \\ {T_{A}{Misc}} \\ {T_{{CL}\; 1}{Misc}} \end{bmatrix}}} & \lbrack 5\rbrack \end{matrix}$ with the offset motor torques based upon inputs including the operating range state of the transmission 10, the input torque and terms based upon system inertias, system damping, and clutch slippage (‘T_(A) Misc’, ‘T_(B) Misc’, ‘T_(CL1) Misc’) combined into a single vector.

For an input torque T_(I), Eq. 5 reduces to Eq. 6 as follows.

$\begin{matrix} {\begin{bmatrix} T_{A} \\ T_{B} \\ T_{{CL}\; 1} \end{bmatrix} = {{\begin{bmatrix} k_{T_{A}{From}\mspace{11mu} T_{O}} \\ k_{T_{B}{From}\mspace{11mu} T_{O}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{O}} \end{bmatrix}T_{O}} + \begin{bmatrix} {T_{A}{Offset}} \\ {T_{B}{Offset}} \\ {T_{{CL}\; 1}{Offset}} \end{bmatrix}}} & \lbrack 6\rbrack \end{matrix}$

Eq. 6 can be solved using the preferred output torque (‘To Opt’) to determine preferred motor torques from the first and second electric machines 56 and 72 (‘T_(A) Opt’, ‘T_(B) Opt’) (550). Preferred battery powers (‘P_(BAT)Opt’, ‘P_(A) Opt’, ‘P_(B) Opt’) can be calculated based thereon (560).

When the transmission 14 is in one of the fixed gear operating range states the linear equation for the system is set forth in Eq. 7.

$\begin{matrix} {\left\lbrack \begin{matrix} T_{O} \\ T_{{CL}\; 1} \\ T_{{CL}\; 2} \end{matrix} \right\rbrack = {{\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{A}} & k_{T_{O}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{B}} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} T_{A} \\ T_{B} \end{matrix} \right\rbrack} + {\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{I}} \end{matrix} \right\rbrack T_{I}} + {\begin{bmatrix} {a\; 11} \\ {a\; 21} \\ {a\; 31} \end{bmatrix}*N_{I}} + {\left\lbrack \begin{matrix} {b\; 11} \\ {b\; 21} \\ {b\; 31} \end{matrix} \right\rbrack*{Nidot}} + {\begin{bmatrix} {c\; 11} & {c\; 12} \\ {c\; 21} & {c\; 22} \\ {c\; 31} & {c\; 32} \end{bmatrix}*\begin{bmatrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \end{bmatrix}}}} & \lbrack 7\rbrack \end{matrix}$

Eq. 7 can be solved to determine an output torque which minimizes the battery power and meets the operator torque request. The T_(CL1) and T_(CL2) terms represent reactive torque transfer across the applied clutches for the fixed gear operation. The terms Tcs1 and Tcs2 represent torque transfer across the non-applied, slipping clutches for the specific fixed gear operation.

The term

$\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{I}} \end{matrix} \right\rbrack*T_{I}$ represents contributions to the output torque To and the reactive torque transfer across the applied clutches T_(CL1) and T_(CL2) due to the input torque T_(I). The scalar terms are based upon the output torque and the reactive torques of the applied clutches related to the input torque (‘k_(To from TI)’, ‘k_(TCL1 from TI)’, ‘k_(TCL2 from TI)’) determined for the specific system application.

The term

$\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{A}} & k_{T_{O}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{B}} \end{matrix} \right\rbrack*\left\lbrack \begin{matrix} T_{A} \\ T_{B} \end{matrix} \right\rbrack$ represents contributions to the output torques and the reactive torque transfer across the applied clutches due to the motor torques T_(A) and T_(B). The scalar terms are based upon the output torque and the reactive torque of the applied clutches related to the torque outputs from the first and second electric machines 56 and 72 determined for the specific system application.

The term

$\left\lbrack \begin{matrix} {b\; 11} \\ {b\; 21} \\ {b\; 31} \end{matrix} \right\rbrack*{Nidot}$ represents contributions to the output torques and the reactive torque transfer across the applied clutches (TCL1, TCL2) due to system inertias, having a single degree of freedom. The input acceleration term is selected as a linearly independent system acceleration which can be used to characterize the inertias of the components of the powertrain system. The b11-b31 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {a\; 11} \\ {a\; 21} \\ {a\; 31} \end{bmatrix}*N_{I}$ represents contributions to the output torques and the reactive torque transfer across the applied clutches T_(CL1) and T_(CL2) due to linear damping, having a single degree of freedom, selected as a linearly independent system speed which can be used to characterize the damping of the components of the powertrain system. The a11-a31 terms are system-specific scalar values determined for the specific system application.

The term

$\begin{bmatrix} {c\; 11} & {c\; 12} \\ {c\; 21} & {c\; 22} \\ {c\; 31} & {c\; 32} \end{bmatrix}*\begin{bmatrix} {{Tcs}\; 1} \\ {{Tcs}\; 2} \end{bmatrix}$ represents contributions to the output torque and the reactive torque transfer across the applied clutches T_(CL1) and T_(CL2) due to non-applied, slipping clutch torques. The Tcs1 and Tcs2 terms represent clutch torques across the non-applied, slipping torque transfer clutches. The c11-c32 terms are system-specific scalar values determined for the specific system application.

Eq. 7 can be rewritten as Eq. 8:

$\begin{matrix} {\left\lbrack \begin{matrix} T_{O} \\ T_{{CL}\; 1} \\ T_{{CL}\; 2} \end{matrix} \right\rbrack = {{\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{A}} & k_{T_{O}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{B}} \end{matrix} \right\rbrack\left\lbrack \begin{matrix} T_{A} \\ T_{B} \end{matrix} \right\rbrack} + {\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{I}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{I}} \end{matrix} \right\rbrack T_{I}} + \left\lbrack \begin{matrix} k_{T_{O}{Misc}} \\ k_{T_{{CL}\; 1}{Misc}} \\ k_{T_{{CL}\; 2}{Misc}} \end{matrix} \right\rbrack}} & \lbrack 8\rbrack \end{matrix}$

For an input torque T_(I), Eq. 8 can be rewritten as Eq. 9:

$\begin{matrix} {\left\lbrack \begin{matrix} T_{O} \\ T_{{CL}\; 1} \\ T_{{CL}\; 2} \end{matrix} \right\rbrack = {{\left\lbrack \begin{matrix} k_{T_{O}{From}\mspace{11mu} T_{A}} & k_{T_{O}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 1}{From}\mspace{11mu} T_{B}} \\ k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{A}} & k_{T_{{CL}\; 2}{From}\mspace{11mu} T_{B}} \end{matrix} \right\rbrack\left\lbrack \begin{matrix} T_{A} \\ T_{B} \end{matrix} \right\rbrack} + \begin{bmatrix} {T_{O}{Offset}} \\ {T_{{CL}\; 1}{Offset}} \\ {T_{{CL}\; 2}{Offset}} \end{bmatrix}}} & \lbrack 9\rbrack \end{matrix}$ with the output torque and the reactive torque transfer across the applied clutches T_(CL1) and T_(CL2) based upon the motor torques with the operating range state of the transmission 10, and terms based upon input torque, system inertias, system damping, and clutch slippage (‘To Offset’, ‘T_(CL1) Offset’, ‘T_(CL2) _(—) Offset’) combined into a single vector. Eq. 9 can be solved using the preferred output torque (‘To Opt’) to determine preferred motor torques from the first and second electric machines 56 and 72, including determining preferred motor torque split (‘T_(A)Opt’, ‘T_(B)Opt’) (550).

The motor torque commands can be used to control the first and second electric machines 56 and 72 to transfer output torque to the output member 64 and thence to the driveline 90 to generate tractive torque at wheel(s) 93 to propel the vehicle in response to the operator input to the accelerator pedal 113. Preferably, propelling the vehicle results in vehicle acceleration so long as the output torque is sufficient to overcome external loads on the vehicle, e.g., due to road grade, aerodynamic loads, and other loads.

Each of Eqs. 3, 4, and 7 can be solved to determine a preferred output torque which minimizes the battery power and meets the operator torque request, and can then be executed to determine preferred motor torques for the first and second electric machines, subject to the clutch constraints.

It is understood that modifications are allowable within the scope of the disclosure. The disclosure has been described with specific reference to the preferred embodiments and modifications thereto. Further modifications and alterations may occur to others upon reading and understanding the specification. It is intended to include all such modifications and alterations insofar as they come within the scope of the disclosure. 

1. Method for controlling a powertrain system including a transmission device operative to transfer power between an input member and a plurality of torque machines and an output member, the torque machines connected to an energy storage device and the transmission device operative in one of a plurality of fixed gear and continuously variable mode operating range states, the method comprising: monitoring available power from the energy storage device; determining system constraints; executing an optimization algorithm to determine constraints on an output torque to the output member comprising a maximum output torque, a minimum output torque, and a preferred output torque in response to the system constraints and the available power from the energy storage device; determining an operator torque request including an acceleration request and a braking request; determining a net output torque command in response to the acceleration request and the braking request and constrained within the maximum output torque and the minimum output torque; executing the optimization algorithm to determine preferred torque commands for each of the torque machines based upon the net output torque command and in response to the system constraints and the available power from the energy storage device; and controlling operation of the torque machines in response to the preferred torque commands.
 2. The method of claim 1, wherein determining the operator torque request including the acceleration request and the braking request comprises determining the acceleration request in response operator input to an accelerator pedal and determining the braking request in response to an operator input to a brake pedal.
 3. The method of claim 1, wherein executing the optimization function to determine the constraints on the output torque to the output member in response to the system constraints and the available power from the energy storage device comprises executing the optimization function to determine the constraints on the output torque to the output member in response to the system constraints and the available power from the energy storage device for the transmission operating range states including the continuously variable mode operating range state and the fixed gear operating range state.
 4. The method of claim 3, wherein adjusting the preferred torque commands for each of the torque machines in response to autonomic control inputs comprises adjusting the preferred torque commands for each of the torque machines in response to one of closed-loop commands, active damping commands and engine pulse cancellation commands.
 5. The method of claim 1, wherein controlling operation of the torque machines in response to the preferred torque commands further comprises: adjusting the preferred torque commands for each of the torque machines in response to autonomic control inputs; and controlling operation of the torque machines in response to the adjusted preferred torque commands.
 6. The method of claim 1, further comprising determining a preferred regenerative braking torque capacity in response to the preferred output torque and the acceleration request.
 7. Method for controlling a powertrain system including a transmission device configured to transfer power between an input member and a plurality of torque machines and an output member, the torque machines connected to an energy storage device and the transmission device operative in one of a plurality of fixed gear and continuously variable mode operating range states by selectively applying torque transfer clutches, the method comprising: monitoring the input member; determining system inputs and system constraints; monitoring available power from the energy storage device; determining a present operating range state for the transmission device; executing an optimization algorithm to determine constraints on an output torque transferred to the output member based upon the system inputs, the system constraints and the available power from the energy storage device; determining an operator torque request; determining an output torque command based upon the constraints on the output torque and the operator torque request; executing the optimization algorithm to determine preferred torque commands for each of the torque machines in response to the output torque command; and controlling operation of the torque machines in response to the preferred torque commands; monitoring the input member to determine an input acceleration profile for the input member and determining a clutch slip acceleration profile for one of the torque transfer clutches; and executing the optimization algorithm to determine the constraints on the output torque transferred to the output member based upon the input acceleration profile, the clutch slip acceleration profile, the system constraints, and the available power from the energy storage device.
 8. The method of claim 7, further comprising determining a range of output torques which react with the output member based upon the range of power outputs from the energy storage device, the input torque from the engine and torque transfer across the selectively applied torque transfer clutches.
 9. The method of claim 7, wherein determining the system constraints comprises determining ranges of reactive clutch torques for the selectively applied torque transfer clutches.
 10. The method of claim 9, wherein executing the optimization algorithm to determine the constraints on the output torque transferred to the output member based upon the system inputs, the system constraints and the available power from the energy storage device comprises executing the optimization function to determine the constraints on the output torque transferred to the output member based upon the system inputs, the system constraints comprising the ranges of reactive clutch torques for the selectively applied torque transfer clutches and the available power from the energy storage device.
 11. Method for controlling a powertrain system including an electro-mechanical transmission device operative to transfer power between an input member and first and second electric machines and an output member, the first and second electric machines connected to an energy storage device and the transmission device operative in one of a plurality of operating range states by selectively applying torque transfer clutches, the method comprising: determining motor torque constraints and reactive torque constraints for applied torque transfer clutches; determining available power from the energy storage device; executing an optimization algorithm to determine constraints on an output torque to the output member based upon the motor torque constraints, the reactive torque constraints for the applied torque transfer clutches and the available power from the energy storage device; determining an operator torque request; executing the optimization algorithm to determine an output torque command based upon the constraints on the output torque to the output member and the operator torque request; determining preferred torque commands for each of the torque machines based upon the output torque command; determining an input acceleration profile for the input member and a clutch slip acceleration profile for one of the torque transfer clutches; and executing the optimization algorithm to determine the constraints on the output torque to the output member based upon the input acceleration profile, the clutch slip acceleration profile, the motor torque constraints and reactive torque constraints for the applied torque transfer clutches, and the available power from the energy storage device.
 12. The method of claim 11, wherein determining the operator torque request comprises determining an operator torque request for braking and determining an operator torque request for acceleration. 